EP2527147A1 - Système de thermorégulation pour presses avec différents niveaux de température - Google Patents

Système de thermorégulation pour presses avec différents niveaux de température Download PDF

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Publication number
EP2527147A1
EP2527147A1 EP12004875A EP12004875A EP2527147A1 EP 2527147 A1 EP2527147 A1 EP 2527147A1 EP 12004875 A EP12004875 A EP 12004875A EP 12004875 A EP12004875 A EP 12004875A EP 2527147 A1 EP2527147 A1 EP 2527147A1
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EP
European Patent Office
Prior art keywords
temperature
heat
tempering
arrangement
heat exchange
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EP12004875A
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German (de)
English (en)
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EP2527147B1 (fr
Inventor
Andreas Harig
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Technotrans SE
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Technotrans SE
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/22—Means for cooling or heating forme or impression cylinders

Definitions

  • the invention relates to an arrangement on a printing machine for temperature control of operating points of the printing press with different operating temperatures.
  • the DE 10316860 and the WO 2006072558 publish system with a heat recovery.
  • a first aspect of the invention relates to an arrangement on a printing machine comprising at least one low-temperature tempering point (NT tempering point), at least one middle temperature tempering point (MT tempering point) and at least one high-temperature tempering point (HT tempering point), which are at a low temperature range ( NT range), a medium temperature range (MT range) and at least one high temperature range (HT range) of a printing press are arranged and designed such that by means of the NT temperature control of the NT range to a low temperature, by means of the MT temperature of the MT Can be temperature-controlled to a middle temperature and by means of the HT tempering point of the HT range to a high temperature, wherein the low temperature is lower than the middle temperature and the middle temperature is lower than the high temperature, wherein the arrangement has a central heat exchange system, which is designed such that the NT tempering point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central heat exchange system can be flow
  • the embodiment according to the invention has the advantage that heat which has been transferred to the heat exchange fluid can be made available to other temperature control points which are to be heated. This can be advantageous, in particular, during a start-up process in which various areas have not yet been brought to operating temperature.
  • a secondary circuit is preferably part of the central heat exchange system or another closed circuit which is in heat exchanging relationship with the central heat exchange system.
  • each of the temperature control can be designed as a directly through a process means, in particular the heat exchange fluid in the central heat exchange system, flowed through circuit, such that the heat flow is transmitted together with the circulating in the circuit processing means, so that the heat flow coupled to the flowing carrier mass of the process medium flow is.
  • Process fluids are any fluids that are supplied to the operation of printing presses and / or circulated in the printing presses, in particular dampening solution, gear oil and / or other fluids which are used for cooling certain components.
  • a separate primary circuit in the sense described may be designed as an open primary circuit in which the fluid is partially consumed at the temperature control point, such as e.g. in fountain solution, or as a closed primary circuit, in which at each point of the primary circuit, the inflow is equal to the outflow.
  • Fountain solution is used on printing machines, inter alia, to wet the non-printing areas of a printing plate, so as to prevent ink acceptance in these areas. Excess fountain solution is collected and returned to the circulation. Since fountain solution often contains volatiles, fountain solution is usually cooled to low temperatures before it is applied to the printing plates. As a result, evaporation of the volatile components is significantly reduced, although not completely prevented.
  • This area of a printing press will generally be an NT area within the meaning of the invention, which is tempered by the NT tempering point. Since at this point, as just described, dampening water is only partially recycled, as far as it was not consumed, this cycle is referred to as "open".
  • such an NT region can also be tempered by a preferably closed circuit, for example by a circuit in the interior of a printing cylinder.
  • This preferred closed circuit would be Part of the NT tempering point and could be tempered in the described case preferably also with fountain solution but also with another process agent.
  • the transfer of heat between the tempering and the central heat exchange system is preferably carried out without converting the form of energy thermal energy into electrical energy or other forms of energy.
  • This consideration also applies to the interposition of a chiller.
  • the refrigerant absorbs heat by evaporation, the refrigerant is further heated during compression and then passes through a heat exchanger, the entire excess heat to the environment or to the heat exchange fluid.
  • only “additional" heat is generated by the mechanical energy in the compressor. Even when using a chiller, therefore, the already absorbed heat is not converted but is still present in the refrigerant and is discharged from this as part of the waste heat to the heat exchange system.
  • the difference between the NT region and the MT region is preferably at least 5 ° C.
  • the difference between the MT range and the HT range is preferably at least 10 ° C.
  • the operating temperature of the NT range between 5 ° C and 15 ° C is particularly preferably in the range of about 10 ° C.
  • Such an operating temperature is suitable for printing presses, in particular in the area of a dampening system.
  • the operating temperature is preferably between 15 ° C and 30 ° C, more preferably in the range of about 20 ° C and 25 ° C.
  • Such a range of possible operating temperatures is used in printing presses, for example in the printing area of a printing machine, in particular on the distributor rollers and / or the ductor rollers.
  • the operating temperature of the HT range is preferably between 45 ° C and 75 ° C and more preferably in the range between about 50 ° C and 65 ° C.
  • Such a temperature range is used, for example, in UV dryers (operating temperature about 60 ° C), on sheet baffles (operating temperature about 50 ° C) and in the cooling of blown air or compressed air used (operating temperature between 60 ° C and 90 ° C).
  • the arrangement further comprises a cold generator, which is arranged and arranged such that by means of the cold generator, the NT tempering is temperature controlled.
  • a cold generator preferably has a chiller, more preferably a compressor-driven chiller with a condenser.
  • a further advantageous embodiment relates to an arrangement in which both the NT temperature control point and the MT temperature control point can be tempered by means of the cold generator.
  • such an arrangement has a design in which the cold generator is arranged such that the waste heat flow generated by the cold generator is directly transferable to the heat exchange fluid in the central heat exchange system.
  • a cooling device is preferably formed by a heat exchanger or has a heat exchanger, via which the resulting heat flow can be discharged to the environment.
  • a heat exchanger may for example be a free cooler.
  • free-cooler temperature control device is meant a device which exploits approximately the temperature of the ambient air in order to cool the heat exchange fluid.
  • the heat exchange fluid may for example flow directly through the cooling device or be connected via an additional heat exchanger with this.
  • a freecooler can preferably be designed as Adiabatkemaschineer which is provided with a liquid application device, in particular a spray device, wherein liquid can be applied to areas of Adiabatkemaschineers, so that by an evaporation of the liquid, the cooling capacity can be increased and / or cooled to lower temperatures , In this case, it is preferred if the liquid can be applied controlled by parameters, for example if a greater cooling capacity is required and / or if a reduction of the cooling temperature is required, for example if the outside temperature is too high.
  • a cooling device may also comprise a liquid / liquid heat exchanger, which is cooled, for example, with groundwater or the like; Etc.
  • a further advantageous embodiment relates to such an arrangement in which both the HT tempering point and the MT tempering point can be tempered by means of the cooling device.
  • such an arrangement preferably has a design in which the cooling device in the operating state of the printing press is in permanently cooling relationship with the HT tempering point.
  • the cooling relationship is preferably such that a waste heat flow of the MT temperature control point to the refrigerator and / or the cooling device can be discharged.
  • a further advantageous embodiment relates to such an arrangement in which a heat flow from the MT tempering point and / or the HT tempering point to the cooling device via the heat exchange fluid in the central heat exchange system is transferable.
  • the arrangement further comprises a cold producer, which is arranged and arranged such that by means of the cold generator of the MT temperature control point is temperature controlled.
  • the refrigeration producer preferably comprises a refrigerator, more preferably a compressor driven refrigerator with an evaporator and a condenser and more preferably an air cooled refrigerator.
  • a further advantageous embodiment relates to an arrangement in which by means of the cold producer both the MT tempering point and the NT tempering point is temperature controlled.
  • such an arrangement has a design in which the cold producer is arranged such that the waste heat flow generated by the cold producer is directly transferable to the heat exchange fluid in the central heat exchange system.
  • the cold generator and the cold producer are operated with refrigerants having different evaporation temperatures and / or different condensation temperatures.
  • a further advantageous embodiment relates to such an arrangement in which the central heat exchange system has a heat exchange circuit with a central inlet and a central outlet, wherein extending between the central inlet and the central outlet a plurality of parallel partial branches, wherein a partial feed of a partial branch to one of Temperature control points runs, wherein a partial flow of a partial branch of the tempering leads coming to the central outlet, such that a central heat exchange fluid flow in the central inlet into different heat exchange fluid partial streams can be divided, the different heat exchange fluid partial streams are different Temperierstellen zuleitbar and wherein the different heat exchange fluid partial streams coming from the different tempering in the central flow are again merge to the central heat exchange fluid flow.
  • the central heat exchange fluid flow in the central inlet and in the partial feeds has the same temperature.
  • the temperatures in the sub-sequences differ depending on the operating temperature of the operating points.
  • the partial fluid flows in the partial drains are mixed in the respective sections of the central drain, so that a different temperature prevails in these sections, until finally merge in the flow direction behind the last partial flow all heat exchange fluid partial streams in the last section of the central process.
  • valve is preferably in Dependent on the operating temperature and the temperature of the incoming central heat exchange fluid flow and / or the incoming heat exchange fluid partial flow, the valve is preferably closed, when the temperature of the incoming central heat exchange fluid flow and / or the incoming heat exchange fluid partial flow is higher than the (actual or desired ) Operating temperature at the operating point.
  • such an arrangement preferably has a design in which at least part of the heat flow transferred to the heat exchange fluid can be dissipated to a heat consumer.
  • heat consumers may e.g. a heater for a Farbreibertemperier réelle and / or a preheating device for preheating thermo air, which, e.g. can be used for drying the printed substrate. Also conceivable are any other heat consumers.
  • the part of the heat flow in the partial sequence of a sub-branch can be removed.
  • the part of the heat flow is taken in a partial branch, which has a suitable temperature level for the respective heat consumer.
  • the part of the heat flow is preferably taken in a partial branch with a high temperature level, in particular in the partial outlet behind the HT tempering point since at this point of the central heat exchange system i.d.R. the highest temperature level prevails.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers at different points of the central heat exchange system with different temperature levels can be dissipated.
  • a further advantageous embodiment relates to such an arrangement in which the cooling device is flowed through directly by the heat exchange fluid flow, wherein the heat exchange fluid flow can be conducted past the cooling device via a bypass line which can be controlled by a bypass valve.
  • Cooling device has a separate cooling circuit, which is connected via a heat exchanger with the heat exchange fluid flow in heat exchanging relationship, wherein the separate cooling circuit is controlled via a cooling circuit valve.
  • a further advantageous embodiment relates to an arrangement in which the bypass valve or the cooling circuit valve can be shut off in the event that the desired operating temperature of one of the temperature control points connected to the central heat exchange system has not yet been reached and / or the temperature in the inlet of the central Heat exchange system is higher than the actual temperature of the respective tempering.
  • such an arrangement has a configuration in which the central heat exchange system is in heat exchanging relationship with individual temperature control circuits hydraulically separated from the central heat exchange system.
  • Hydraulically separated in the sense used here meant, without flow connection, via which a heat flow together with a fluid flow would be transferable.
  • the fluid circuits remain separate and can therefore be e.g. be operated with different tempering fluids. Accordingly, only the respective heat flows are transmitted to the central heat exchange system by the temperature control circuit circuits provided separately in the hydraulic system.
  • a central heat exchanger may be provided, which is in heat exchanging relationship with several or all of the temperature control circuits, wherein the heat flows of the respective temperature control circuits are transferred to a provided in the central heat exchanger heat exchange fluid.
  • the different temperature levels in the temperature control loop are standardized to a temperature of the heat exchange fluid in the central heat exchanger.
  • a separation of one of the tempering point circuits can preferably be configured via a respective bypass line that can be activated via a valve.
  • the valve is preferably designed as a function of the operating temperature at the respective operating point and the temperature of the heat exchange fluid in the central heat exchange system, wherein the valve is preferably closed when the temperature of the heat exchange fluid is higher than the (actual or desired) operating temperature at the operating point ,
  • a further advantageous embodiment relates to such an arrangement in which at least part of the heat flow transferred to the heat exchange fluid can be dissipated to a heat consumer.
  • a heat consumer may e.g. a heater for a Farbreibertemperier réelle and / or preheating device, the e.g. can be used for preheating of thermo air, which e.g. can be used to dry the printed substrate.
  • a configuration of an arrangement in which at least part of a waste heat flow occurring at one of the operating points can be dissipated to a heat consumer is preferred, wherein the arrangement is designed such that this waste heat flow can be dissipated from a point of the respective tempering point circuit which differs from the one Operating point downstream of the central heat exchange system is arranged.
  • a heat consumer heat exchanger is provided for this purpose in the respective temperature control circuit, which is traversed by the respective temperature control in the respective temperature control circuit, which flows in the direction of the central heat exchange system. This transfers the part of the heat flow to the respective feed circuit of the heat consumer.
  • heat can advantageously be taken from that temperature control circuit which has a temperature level suitable for the respective heat consumer.
  • the part of the heat flow is taken in a tempering point circuit with a high temperature level, in particular the tempering point circuit of the HT tempering since this usually has the highest temperature level.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers from different temperature control circuits with different temperature levels can be dissipated.
  • such an arrangement preferably has a design in which the cooling device is flowed through directly by the heat exchange fluid flow, wherein the heat exchange fluid flow can be conducted past the cooling device via a bypass line that can be controlled by a bypass valve.
  • cooling device has a separate cooling circuit, which is in heat exchanging relationship with the heat exchange fluid flow via a heat exchanger, wherein the separate cooling circuit can be controlled via a cooling circuit valve.
  • a further advantageous embodiment relates to such an arrangement in which the bypass valve or the cooling circuit valve can be blocked in the event that the desired operating temperature of one of the temperature control points connected to the central heat exchange system has not yet been reached and / or the temperature in the inlet of the central heat exchange system is higher than the actual temperature of the respective tempering.
  • the arrangement further comprises a buffer memory in which heat is temporarily stored in a heat storage material.
  • a further advantageous embodiment relates to an arrangement in which the heat storage material has a larger amount of heat exchange fluid.
  • such an arrangement has a design in which two central heat exchange systems are provided, one of the two central heat exchange systems is provided for supplying heat consumers with heat, as described in the claims A17 to A21 and A24 to A29 and wherein the other of the two central Heat exchange systems comprising the cooling device.
  • a second aspect of the invention relates to an arrangement on a printing press, comprising at least one low-temperature tempering point (NT tempering point), at least one middle temperature tempering point (MT tempering point) and at least one high-temperature tempering point (HT tempering point), which at a low temperature range (NT area), a middle temperature range (MT range) and at least one high temperature range (HT range) of a printing press are arranged and designed such that means of the NT temperature control of the NT range to a low temperature, by means of the MT temperature MT range can be tempered to a middle temperature and by means of the HT tempering point of the HT range to a high temperature, wherein the low temperature is lower than the middle temperature and the middle temperature is lower than the high temperature, wherein the arrangement further comprises a low-temperature temperature control device (NT temperature control device) and a high-temperature temperature control device (HT temperature control device), wherein the MT tempering point can be tempered both via the NT tempering device and via the HT tempering device
  • the NT temperature control device can be designed, for example, to a low temperature which, depending on the embodiment, for example, an NT tempering point on the printing press anyway, whereas the HT tempering device can be designed so that they energy saving the Ambient temperature can be used for temperature control. Therefore, depending on the ambient temperature and the desired operating temperature, an embodiment according to the invention can advantageously be designed in such a way that the desired operating temperature is achieved under a combination of the two temperature control devices optimized with regard to desired power and optimum energy utilization becomes.
  • an essential component of the HT temperature control device is preferably a free cooler.
  • the various temperature levels herein are referred to by the terms “high”, “medium” and “low” only for the purpose of indicating a not insignificant difference between the operating temperatures. Moreover, the terms have no quantitative significance.
  • the difference between the NT region and the MT region is preferably at least 5 ° C.
  • the difference between the MT range and the HT range is preferably at least 10 ° C.
  • the operating temperature of the NT range between 5 ° C and 15 ° C is particularly preferably in the range of about 10 ° C. Such an operating temperature is suitable for printing presses, in particular in the area of a dampening system.
  • the operating temperature is preferably between 15 ° C and 30 ° C, more preferably in the range of about 20 ° C and 25 ° C.
  • the operating temperature of the HT range is preferably between 45 ° C and 75 ° C and more preferably in the range between about 50 ° C and 65 ° C.
  • Such a temperature range comes e.g. 60 ° C), sheet baffles (operating temperature approx. 50 ° C) and cooling of blown air or compressed air (operating temperature between 60 ° C and 90 ° C).
  • NT temperature control device and the HT temperature control device are connected to the MT temperature control point such that the MT temperature control point can be temperature controlled simultaneously by the NT temperature control device and the HT temperature control device.
  • a further advantageous embodiment relates to an arrangement in which the NT tempering device and the HT tempering device are connected to the MT tempering point such that the MT tempering point depends on certain parameters at a certain time either by the NT tempering device or the HT tempering device is temperature controlled.
  • Such parameters may, for example, the actual and / or desired temperature of the MT operating point and / or achievable by the HT tempering device Be tempering. This temperature range may in turn depend on the temperature of a heat exchange fluid. It is also conceivable that if the HT temperature control device is a free-cooling device, as described above, such a parameter is the ambient temperature around the free cooler.
  • such an arrangement has a design in which the NT temperature control device has a cold generator.
  • a cold generator preferably has a chiller, more preferably a compressor-driven chiller with a condenser.
  • the arrangement further comprises a central heat exchange system, which is designed such that the NT temperature control point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central Heat exchange system can be traversed by a heat exchange fluid, and wherein the heat exchange system with the NT tempering point, the MT tempering point and the HT tempering point is in communication such that heat flows both between the NT tempering and the heat exchange fluid, as well as between the MT tempering and the heat exchange fluid as well as between the HT tempering point and the heat exchange fluid are transferable.
  • a central heat exchange system which is designed such that the NT temperature control point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central Heat exchange system can be traversed by a heat exchange fluid, and wherein the heat exchange system with the NT tempering point, the MT tempering point and the HT tempering point is in communication such that heat flows both between the
  • the transfer of heat between the tempering and the central heat exchange system is preferably carried out without converting the form of energy thermal energy into electrical energy or other forms of energy.
  • This also applies to the interposition of a chiller.
  • the refrigerant absorbs heat by evaporation, the refrigerant is further heated during compression (mechanical energy) and then passes through a heat exchanger, the entire excess heat to the environment or to the heat exchange fluid.
  • mechanical energy mechanical energy
  • only “additional" heat is generated by the mechanical energy in the compressor. Even when using a chiller, therefore, the already absorbed heat is not converted but is still present in the refrigerant and is discharged from this as part of the waste heat to the heat exchange system.
  • a further advantageous embodiment relates to an arrangement in which the cold generator is arranged such that the waste heat flow generated by the cold generator is directly transferable to the heat exchange fluid in the central heat exchange system.
  • such an arrangement has a design in which the HT tempering device has a cooling device.
  • a cooling device is preferably formed by a heat exchanger or has a heat exchanger, via which the resulting heat flow can be discharged to the environment.
  • a heat exchanger may e.g. to be a free cooler.
  • free-cooler temperature control device is meant a device which exploits approximately the temperature of the ambient air in order to cool the heat exchange fluid.
  • the heat exchange fluid may be e.g. to be a process agent. Process fluids are any fluids that are supplied to the operation of printing presses and / or circulated in the printing presses, in particular dampening solution, gear oil and / or other fluids which are used for cooling certain components.
  • a freecooler can preferably be designed as Adiabatkemaschineer which is provided with a liquid application device, in particular a spray device, wherein liquid can be applied to areas of Adiabatkemaschineers, so that by an evaporation of the liquid, the cooling capacity can be increased and / or cooled to lower temperatures , In this case, it is preferred if the liquid can be applied under the control of parameters, e.g. if greater cooling capacity is required and / or if a reduction in the cooling temperature is required, e.g. when the outside temperature is too high.
  • a cooling device may also comprise a liquid / liquid heat exchanger, e.g. is cooled with groundwater or the like; Etc.
  • the cold generator is in a permanently cooling relationship to the NT temperature control point in the operating state of the printing machine.
  • a further advantageous embodiment relates to such an arrangement in which the cooling device in the operating state of the printing press is in a permanently cooling relationship with the HT tempering point.
  • the arrangement further comprises a central heat exchange system, which is designed such that the NT temperature control point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central Heat exchange system can be traversed by a heat exchange fluid, and wherein the heat exchange system with the NT tempering point, the MT tempering point and the HT tempering point is in communication such that heat flows both between the NT tempering and the heat exchange fluid, as well as between the MT tempering and the heat exchange fluid as well as between the HT tempering point and the heat exchange fluid are transferable.
  • a central heat exchange system which is designed such that the NT temperature control point, the MT tempering point and the HT tempering are temperature controlled via the central heat exchange system, wherein a pipe system of the central Heat exchange system can be traversed by a heat exchange fluid, and wherein the heat exchange system with the NT tempering point, the MT tempering point and the HT tempering point is in communication such that heat flows both between the
  • a further advantageous embodiment relates to an arrangement in which the arrangement is designed such that a heat flow from the MT tempering point and / or the HT tempering point to the cooling device via the heat exchange fluid in the central heat exchange system is transferable.
  • such an arrangement has a design in which the arrangement further comprises a refrigeration producer, which is arranged and arranged such that the MT temperature control point can be tempered by means of the cold generator.
  • the refrigeration producer preferably comprises a refrigerator, more preferably a compressor driven refrigerator with an evaporator and a condenser and more preferably an air cooled refrigerator.
  • both the MT tempering point and the NT tempering point can be tempered by means of the cold producer.
  • a further advantageous embodiment relates to such an arrangement in which the cold producer is arranged such that the waste heat flow generated by the cold producer is directly transferable to the heat exchange fluid in the central heat exchange system.
  • such an arrangement preferably has a configuration in which the central heat exchange system has a heat exchange circuit with a central inlet and a central outlet, wherein extending between the central inlet and the central outlet a plurality of parallel partial branches, wherein a partial feed of a partial branch to a the temperature control points, wherein a partial flow of a partial branch of the tempering leads to the central drain, such that a central heat exchange fluid flow in the central inlet into different heat exchange fluid partial streams can be divided, wherein the different heat exchange fluid partial streams different Temperierstellen zuleitbar and wherein the different heat exchange fluid partial streams of the different tempering coming in the central process again to the central heat exchange fluid flow are merge.
  • the central heat exchange fluid flow in the central inlet and in the partial feeds has the same temperature.
  • the temperatures in the sub-sequences differ depending on the operating temperature of the operating points.
  • the partial fluid flows in the partial drains are mixed in the respective sections of the central drain, so that a different temperature prevails in these sections, until finally merge in the flow direction behind the last partial flow all heat exchange fluid partial streams in the last section of the central process.
  • the valve is actuatable depending on the operating temperature at the point of operation and the temperature of the incoming central heat exchange fluid stream and / or the incoming heat exchange fluid sub-stream, preferably closing the valve when the temperature of the incoming central heat exchange fluid stream and / or the incoming heat exchange fluid sub-stream is higher as the (actual or desired) operating temperature at the site.
  • a further advantageous embodiment relates to such an arrangement in which at least a portion of the heat flow transferred to the heat exchange fluid can be dissipated to a heat consumer.
  • heat consumers may e.g. a heater for a Farbreibertemperier réelle and / or a preheating device for preheating thermo air, which, e.g. can be used for drying the printed substrate. Also conceivable are any other heat consumers.
  • a further advantageous embodiment relates to such an arrangement in which the dissipatable part of the heat flow in the partial sequence of a sub-branch can be removed.
  • the part of the heat flow is taken in a partial branch, which has a suitable temperature level for the respective heat consumer.
  • the part of the heat flow is preferably taken in a partial branch with a high temperature level, in particular in the partial outlet behind the HT tempering point since at this point of the central heat exchange system i.d.R. the highest temperature level prevails.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers at different points of the central heat exchange system with different temperature levels can be dissipated.
  • cooling device is flowed through directly by the heat exchange fluid flow and in which the heat exchange fluid flow can be conducted past the cooling device via a bypass line which can be activated by means of a bypass valve is preferred.
  • a further advantageous embodiment relates to an arrangement in which the cooling device has a separate cooling circuit, which is in heat exchanging relationship with the heat exchange fluid flow via a heat exchanger, wherein the separate cooling circuit is controllable via a cooling circuit valve.
  • such an arrangement has a design in which the Bypass valve or the cooling circuit valve can be shut off in the event that the desired operating temperature of one of the temperature control points connected to the central heat exchange system has not yet been reached and / or the temperature in the inlet of the central heat exchange system is higher than the actual temperature of the respective temperature control point.
  • the central heat exchange system is in heat exchanging relationship with individual temperature control loop circuits hydraulically separated from the central heat exchange system.
  • Hydraulically separated in the sense used here meant, without flow connection, via which a heat flow together with a fluid flow would be transferable.
  • the fluid circuits remain separate and can therefore be e.g. be operated with different tempering fluids. Accordingly, only the respective heat flows are transmitted to the central heat exchange system by the temperature control circuit circuits provided separately in the hydraulic system.
  • a central heat exchanger may be provided, which is in heat exchanging relationship with several or all of the temperature control circuits, wherein the heat flows of the respective temperature control circuits are transferred to a provided in the central heat exchanger heat exchange fluid.
  • the different temperature levels in the temperature control loop are standardized to a temperature of the heat exchange fluid in the central heat exchanger.
  • a further advantageous embodiment relates to such an arrangement in which the heat exchanging relationship between one of the separate Temperierstellen circuits and the central heat exchange system is designed separable, such that from the Temperierstellen cycle to the central heat exchange system no heat flow is more transferable.
  • a separation of one of the tempering point circuits can preferably be configured via a respective bypass line that can be activated via a valve.
  • the valve is preferably in dependence on the operating temperature at the respective operating point and the temperature of the heat exchange fluid in the central Heat exchanging system designed controllable, wherein the valve is preferably closed when the temperature of the heat exchange fluid is higher than the (actual or desired) operating temperature at the operating point.
  • heat consumers may e.g. a heater for a Farbreibertemperier réelle and / or a preheating device for preheating thermo air, which, e.g. can be used for drying the printed substrate. Also conceivable are any other heat consumers.
  • such an arrangement preferably has a design in which at least part of a waste heat flow occurring at one of the operating points can be dissipated to a heat consumer, the arrangement being designed such that this waste heat flow can be dissipated from a point of the respective temperature control circuit which from the operating point downstream of the central heat exchange system is arranged.
  • a heat consumer heat exchanger is provided for this purpose in the respective temperature control circuit, which is traversed by the respective temperature control in the respective temperature control circuit, which flows in the direction of the central heat exchange system. This transfers the part of the heat flow to the respective feed circuit of the heat consumer.
  • heat can advantageously be taken from that temperature control circuit which has a temperature level suitable for the respective heat consumer.
  • the part of the heat flow is taken in a tempering point circuit with a high temperature level, in particular the tempering point circuit of the HT tempering since da i.d.R. has the highest temperature level.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers from different temperature control circuits with different temperature levels can be dissipated.
  • Cooling device is directly traversed by the heat exchange fluid flow, wherein the heat exchange fluid flow is passed over a controllable with a bypass valve by-pass line to the cooling device.
  • a further advantageous embodiment relates to such an arrangement in which the cooling device has a separate cooling circuit, which is in heat exchanging relationship with the heat exchange fluid flow via a heat exchanger, wherein the separate cooling circuit can be controlled via a cooling circuit valve.
  • bypass valve or the cooling circuit valve can be shut off in the event that the desired operating temperature of one of the temperature control points connected to the central heat exchange system has not yet been reached and / or the temperature in the inlet of the central heat exchange system is higher is the actual temperature of the respective temperature control point.
  • a further advantageous embodiment relates to an arrangement in which the arrangement further comprises a buffer memory in which heat is temporarily stored in a heat storage material.
  • such an arrangement has a configuration in which the heat storage material has a larger amount of heat exchange fluid.
  • a third aspect of the invention relates to an arrangement on a printing press comprising at least one low-temperature tempering point (NT tempering point) and at least one middle temperature tempering point (MT tempering point), which are connected to a low-temperature region (NT region) and a medium-temperature region (MT).
  • NT tempering point low-temperature tempering point
  • MT tempering point middle temperature tempering point
  • NT tempering of the NT range to a low temperature and by means of the MT tempering the MT range is temperature-controlled to a middle temperature, wherein the low temperature is lower than the average temperature, wherein the NT tempering point and the MT tempering point via a central heat exchange system, which is traversed by a heat exchange fluid, are connected to a heat consumer system such that the waste heat flows incurred in the temperature control at the NT tempering and MT tempering, at least partially transferable to the heat consumer system.
  • At least partially transferable in the sense preferably means that at least one partial waste heat flow from each of the two temperature control points can be transmitted to the heat consumption system.
  • the temperature levels herein are referred to by the terms “low” and “medium” only for the purpose of indicating a not insubstantial difference between the operating temperatures. Moreover, the terms have no quantitative significance. Therefore, as long as only two temperature levels are described, the terms described in relation to this aspect of the invention are also replaceable by the terms “medium” and “high” or “low” and “high” described with respect to the other aspects of the invention.
  • the arrangement further has a high-temperature tempering point (HT tempering point) which is arranged on a high-temperature region (HT region) of the printing press and designed such that the HT tempering point of the HT Temperature is tempered to a high temperature, wherein high temperature is higher than the low temperature and higher than the middle temperature.
  • HT tempering point high-temperature tempering point
  • the difference between the NT range and the MT range preferably at least 5 ° C.
  • the difference between the MT range and the HT range is preferably at least 10 ° C.
  • the operating temperature of the NT range between 5 ° C and 15 ° C is particularly preferably in the range of about 10 ° C.
  • Such an operating temperature is suitable for printing presses, in particular in the area of a dampening system.
  • the operating temperature is preferably between 15 ° C and 30 ° C, more preferably in the range of about 20 ° C and 25 ° C.
  • Such a range of possible operating temperatures is used in printing presses, for example in the printing area of a printing machine, in particular on the distributor rollers and / or the ductor rollers.
  • the operating temperature of the HT range is preferably between 45 ° C and 75 ° C and more preferably in the range between about 50 ° C and 65 ° C.
  • Such a temperature range is used, for example, in UV dryers (operating temperature about 60 ° C), on sheet baffles (operating temperature about 50 ° C) and in the cooling of blown air or compressed air used (operating temperature between 60 ° C and 90 ° C).
  • a further advantageous embodiment relates to an arrangement in which the arrangement further comprises a central heat reservoir, wherein heat consumers are connected to the central heat reservoir to which the heat from the central heat reservoir can be dissipated.
  • such an arrangement has a design in which the arrangement is designed such that coming from the tempering, heat-dissipating fluid streams are supplied via Temperierstellen Oberen the central heat exchange system, wherein the fluid streams in the central heat exchange system unite.
  • Temperierstellen Gustaven the central heat exchange system, wherein the fluid streams in the central heat exchange system unite.
  • such an arrangement is preferred in which at least part of a waste heat flow occurring at one of the operating points can be dissipated to a heat consumer, the arrangement being designed such that this waste heat flow or partial waste heat flow can be dissipated from a point of the respective temperature control line, which differs from the one Operating point downstream in front of the central Heat reservoir is arranged.
  • a further advantageous embodiment relates to such an arrangement in which the arrangement is designed such that for at least one of the temperature control points coming, heat-dissipating fluid flows a temperature control circuit is provided which is formed hydraulically separated from the central heat reservoir, so that only a heat flow is transferred from the heat-dissipating fluid flow to the central heat reservoir. Only fluid flow is transferred to the central heat reservoir - but not a fluid flow.
  • the tempering circuit is hydraulically separated from the heat reservoir. As a result, different fluids can preferably be used. Individual temperature control circuits can be hydraulically connected with each other and hydraulically separated from other temperature control circuits.
  • a heat consumer heat exchanger is provided for this purpose in the respective temperature control circuit, which is traversed by the respective temperature control in the respective temperature control circuit, which flows in the direction of the central heat exchange system. This transfers the part of the heat flow to the respective feed circuit of the heat consumer.
  • heat can advantageously be taken from that temperature control circuit which has a temperature level suitable for the respective heat consumer.
  • the part of the heat flow is taken in a tempering point circuit with a high temperature level, in particular the tempering point circuit of the HT tempering since this usually has the highest temperature level.
  • the arrangement is designed such that different parts of the total heat flow for different heat consumers from different temperature control circuits with different temperature levels can be dissipated are.
  • such an arrangement preferably has a configuration in which the heat exchange system communicates with at least two tempering points in such a way that a heat flow from one of the at least two tempering points to the other of the at least two tempering points can be transferred via the heat exchange fluid.
  • the transfer of heat between the tempering and the central heat exchange system is preferably carried out without converting the form of energy thermal energy into electrical energy or other forms of energy. This also applies to the interposition of a chiller. In the chiller, the refrigerant absorbs heat by evaporation, the refrigerant is further heated during compression (mechanical energy) and then passes through a heat exchanger, the entire excess heat to the environment or to the heat exchange fluid.
  • the arrangement further comprises a cold generator, which is arranged and arranged such that by means of the cold generator, the NT tempering is temperature controlled.
  • a refrigerator preferably comprises a refrigerator and more preferably a compressor-driven refrigerator with a condenser.
  • both the NT temperature control point and the MT temperature control point can be tempered by means of the cold generator.
  • a further advantageous embodiment relates to an arrangement in which the cold generator is arranged such that the waste heat flow generated by the cold generator is directly transferable to the heat exchange fluid in the central heat exchange system.
  • Waste heat stream in the sense is to be understood that of the term both the absorbed by the cold generator Heat - ie the "generated" cold - as well as the heat loss produced by the refrigerator is included.
  • such an arrangement has a configuration in which the arrangement further comprises a cooling device .
  • a cooling device is preferably formed by a heat exchanger or has a heat exchanger, via which the resulting heat flow can be discharged to the environment.
  • a heat exchanger may for example be a free cooler.
  • free-cooler temperature control device is meant a device which exploits approximately the temperature of the ambient air in order to cool the heat exchange fluid.
  • the heat exchange fluid may be, for example, a processing agent. Process fluids are any fluids that are supplied to the operation of printing presses and / or circulated in the printing presses, in particular dampening solution, gear oil and / or other fluids which are used for cooling certain components.
  • a freecooler can preferably be designed as Adiabatkemaschineer which is provided with a liquid application device, in particular a spray device, wherein liquid can be applied to areas of Adiabatkemaschineers, so that by an evaporation of the liquid, the cooling capacity can be increased and / or cooled to lower temperatures , In this case, it is preferred if the liquid can be applied controlled by parameters, for example if a greater cooling capacity is required and / or if a reduction of the cooling temperature is required, for example if the outside temperature is too high.
  • a cooling device may also comprise a liquid / liquid heat exchanger, which is cooled, for example, with groundwater or the like; Etc.
  • both the HT tempering point and the MT tempering point can be tempered by means of the cooling device.
  • a further advantageous embodiment relates to such an arrangement in which the cold generator is in the operating condition of the printing press in a permanently cooling relationship with the NT tempering.
  • such an arrangement preferably has a design in which the cold generator and the cooling device can be brought into cooling relationship with the MT tempering point in the operating state of the printing press depending on an ambient temperature around the cooling device.
  • the cooling relationship is preferably such that a waste heat flow of the MT temperature control point to the refrigerator and / or the cooling device can be discharged.
  • a further advantageous embodiment relates to such an arrangement in which the arrangement further comprises a cold producer , which is arranged and arranged such that by means of the cold generator of the MT temperature control point is temperature controlled.
  • a refrigerating producer preferably has a refrigerating machine, more preferably a compressor-driven refrigerating machine with an evaporator and a condenser, more preferably such an air-cooled refrigerating machine.
  • a further advantageous embodiment relates to such an arrangement in which both the MT tempering point and the NT tempering point can be tempered by means of the cold producer.
  • the cold producer is arranged such that the waste heat flow generated by the cold producer is directly transferable to the heat exchange fluid in the central heat exchange system.
  • a further advantageous embodiment relates to an arrangement in which the cold producer and the cold producer with refrigerants with different evaporation temperatures and / or different condensation temperatures operate.
  • such an arrangement has a configuration in which the heat exchange system as described in claims A15 to A28 is described with respect to the heat exchange system.
  • the arrangement further comprises a buffer memory, in which heat is temporarily stored in a heat storage material.
  • a further advantageous embodiment relates to such an arrangement in which the heat storage material has a larger amount of heat exchange fluid and wherein the heat exchange fluid is hydraulically in communication with the heat exchange fluid in the heat exchange system.
  • FIGS. 1 to 3 which are particularly suitable to describe ways of fluid cooling, as well as on the FIGS. 4 and 5 which are particularly suitable to describe ways of supplying heat to consumers.
  • the illustrated embodiments of the FIGS. 1 to 3 are almost arbitrary with the embodiments of FIGS. 4 and 5 to combine.
  • FIG. 1a shows an overview of an inventive arrangement on a printing machine 1 and thus a system with a cold generator, which is preferably designed as a chiller, and a cooling device 3, which is presently designed as a free cooler.
  • the cooling device 3 is preferably an adiabatic free-cooling device, ie a spraying device 31 makes it possible to improve the cooling capacity by means of evaporative cooling.
  • the spraying device can preferably be supplied with water via a water pipe, for example, and is preferably only switched on if an improvement in the cooling capacity is required.
  • the illustrated printing machine has three different regions 11, 12, 13 with three different temperature levels, which can be temperature-controlled via an NT temperature control point 51, an MT temperature control point 52 and an HT temperature control point 53.
  • the NT tempering point 51 and the MT tempering point 52 are in Fig. 1c shown enlarged example.
  • each of the temperature control 51, 52, 53 have a separate primary circuit 81 which is designed so that the heat flow via a heat exchanger 681, 682 to a secondary circuit 82 can be discharged.
  • a separate primary circuit in the sense described may be designed as an open primary circuit in which the fluid is partially consumed at the temperature control point, such as e.g. in fountain solution, or as a closed primary circuit, in which at each point of the primary circuit, the inflow is equal to the outflow.
  • each or some of the temperature control points to have a circuit through which a process fluid flows, such that the heat flow is transmitted together with the circulating process agent, so that the heat flow is coupled to the flowing carrier mass of the process fluid flow.
  • Fig. 1c is exemplified by the lines which reach up to the respective tempering 51, 52 and are shown between the primary circuits 81.
  • Fig. 1c is exemplified by the lines which reach up to the respective tempering 51, 52 and are shown between the primary circuits 81.
  • these lines are components of sub-branches 65 of a central heat exchange system 6, which communicate directly with the heat exchange circuit 62, so that via a central inlet 631 of the heat exchange circuit 62 heat exchange fluid can flow into the partial inlet 651 of the partial branch 65, can reach the tempering and from there via a partial outlet 652 of the partial branch 65 can get back to a central sequence of the heat exchange circuit 62.
  • This design can be formed at the tempering "open" and / or closed.
  • the so-tempered heat exchange fluid can be passed through the heat exchange circuit 62 to other temperature control, which may be useful, for example in the warm-up of a printing press to the still cold other tempering the waste heat of another temperature control available put.
  • This can be done directly via cross connections 653, 654 between the partial branches of the temperature control, as in FIGS. 1 a and 1b is shown by the horizontally illustrated lines, which is exemplified an exchange of heat exchange fluid between the sub-branch of the NT temperature control point and the sub-branch of the MT temperature control point.
  • the transverse connection 653 leads back from the NT temperature control point to the MT temperature control point and the transverse connection 654.
  • valves 661, 664 are provided.
  • a fluid flow could also flow from the central inlet 63 via a section of the cross connection 653 to the heat exchanger 681 of the NT temperature control point in order to cool the NT temperature control point.
  • This can be especially true at low outdoor temperatures, e.g. be useful in winter, when the heat exchange circuit 62 is used for cooling and as shown with a cooling device 3 is in heat exchanging connection.
  • the heat exchange circuit 62 can be connected via the bypass line 67 and the bypass valve 671 for this purpose with the cooling device 3 or shut off from this.
  • the cold generator 2 may be preferable for the cold generator 2 to permanently cool the NT temperature control point, that is, whenever waste heat has to be dissipated.
  • the cold generator 2 is preferably designed to be so powerful that additionally at least part of the heat load of the MT cooling points can be dissipated, e.g. when the free cooler is no longer sufficient when the ambient temperature rises.
  • the intermediate circuit supplies via the cross connections 653, 654 the MT temperature control point to the cooling side of the cold generator 2.
  • the waste heat of the cold generator is preferably dissipated to the heat exchange fluid in the heat exchange circuit 62.
  • a corresponding circulation in the circuits which can change depending on the valve positions their course is preferably generated by circulation pumps, which can be switched on as needed.
  • 3-2 directional valves and associated bypasses ensure a constant temperature at the tempering points, as is illustrated by way of example with respect to the MT tempering point 52 above the heat exchanger 682.
  • the HT tempering point (s) which are to be cooled to a temperature of generally above 50 ° C. are preferably cooled all year round by means of a cooling device 3 designed as a free cooler.
  • a cooling device 3 designed as a free cooler.
  • the other temperature control points which regularly have operating temperatures which can not be cooled or uneconomically cooled all year round via a free cooler, can be shut off in the heat exchange circuit 62 in such a way that too hot a heat exchange fluid does not reach them.
  • tempering is therefore particularly advantageous that all three temperature control with each other either from the cooling capacity and / or participate in the waste heat and / or temperature over an ambient temperature without or with only a little foreign energy.
  • a printing operation will not start until all circuits have reached the desired temperature. This is usually achieved by cooling in the NT circuit and in the MT or possibly in the HT circuit usually by heating.
  • bypass valve 671 is a 3-2 way valve (46) and only passes on so much heat energy to the free cooler that no additional heat energy generated by electric heaters for the temperature of the MT and HT circuits got to.
  • the potential for savings here depends inter alia on the ambient conditions and the actually required temperature levels, especially of the MT cooling points, since the operating temperature of e.g. 20-25 ° C only partially or completely can be generated via the free cooler.
  • FIG. 2 shows a comparable system as in the FIGS. 1a to 1 d. So that duplicate descriptions are avoided.
  • a cold producer 4 is additionally provided, which are both designed as chillers in the illustrated embodiment.
  • Two separate chillers can further optimize the system, since the chillers can be operated at different evaporation temperatures.
  • FIG. 2 it is the chillers to water-cooled systems that deliver their waste heat to the central heat exchange system 6, for example, for further use and / or to the free cooler.
  • FIG. 3 again shows a comparable system as in the FIGS. 1a to 1d and 2 , Again, duplicate descriptions are avoided. Also in the FIG. 3 is in addition to the cold generator 2 in addition a cold producer 4 is provided, which is executed in the illustrated embodiment, however, as air-cooled chillers. Preferably, the air-cooled chiller for the average temperature level is not placed in the same room as the printing press. Again, a free cooler is also provided.
  • the MT and the HT tempering can be connected to the heat exchange circuit 62 via a - with open valve further - partial branch 65 of the heat exchange circuit 62.
  • the air-cooled chiller completely and / or partially connected to it.
  • FIG. 4 shows the arrangement with a common heat recovery through a heat consumer system 9 is supplied with heat.
  • the heat consumer 9 has a common heat exchanger 91, which is housed in the illustrated preferred embodiment in a storage tank which is at least partially filled by a heat storage material, which caches the heat emitted from the heat exchanger.
  • the heat exchanger 91 is therefore designed as a heat reservoir 92 at the same time.
  • the illustrated arrangement may preferably have a cooling system, as in relation to the central heat exchange system 6 in FIGS. 1a to 3 has been described.
  • the heat consumer system 9 shown can also be regarded as a cooling system, since heat is also removed from the printing press via the consumers.
  • the illustrated manner of the line system of the heat consumer 9 and the arrangement of the elements of the leads to the heat consumer 9th can therefore be carried out in the same way in a heat exchange system 6 according to the invention, as well as vice versa.
  • the temperature control with the heat consumer 9 preferably via mutually hydraulically separate temperature control circuits in heat exchanging relationship.
  • the individual hydraulically separated Temperierstellen circuits are preferably exemplified circulation valves 653, 654 the heat exchanger 91 can be switched.
  • a blown air cooling 7 is provided here, which is also connected to the heat exchanger 91.
  • waste heat sources e.g. the water-cooled chiller, a UV dryer, sheet baffles and the blast or compressed air supply 7 connected, since comparatively high temperature levels are generated for a meaningful use.
  • Other waste heat sources are also conceivable.
  • the heat absorbed in the heat reservoir 92 is given off to heat consumers 93 as needed.
  • the different temperature levels in the heat exchanger 91 are combined to a mixing temperature which is higher than the lowest temperature level but lower than the highest temperature level.
  • FIG. 5 shows a similar arrangement with a depending on the temperature level separately usable heat recovery.
  • FIG. 5 As shown embodiment, an example is shown how different temperature levels can be tapped and used separately by means of upstream heat exchangers. Furthermore, after the separate use of the residual heat can be summarized in a waste heat cycle and possibly stored in a downstream heat exchanger and / or buffer tank.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Control Of Temperature (AREA)
  • Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
EP12004875.6A 2007-11-07 2008-11-07 Système de thermorégulation pour presses avec différents niveaux de température Active EP2527147B1 (fr)

Applications Claiming Priority (2)

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DE102007053080A DE102007053080A1 (de) 2007-11-07 2007-11-07 Temperiersystem für Druckmaschinen mit mehreren Temperaturniveaus
EP08847011A EP2209631B1 (fr) 2007-11-07 2008-11-07 Système de thermorégulation pour machines à imprimer, à plusieurs niveaux de température

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EP08847011A Division EP2209631B1 (fr) 2007-11-07 2008-11-07 Système de thermorégulation pour machines à imprimer, à plusieurs niveaux de température
EP08847011.7 Division 2008-11-07

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EP2527147B1 EP2527147B1 (fr) 2014-06-04

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DE102010062144B4 (de) * 2010-11-29 2015-11-12 Koenig & Bauer Ag Druckmaschine mit mindestens einem einen Heißlufttrockner aufweisenden Trocknersystem sowie Verfahren zum Betreiben eines einen Heißlufttrockner aufweisenden Trocknersystems
CN102582237B (zh) * 2012-01-14 2014-04-02 湖南省浏阳市择明热工器材有限公司 一种印刷车间空调制冷和加热固化的复合系统
DE102012014236B3 (de) * 2012-07-18 2013-05-23 Technotrans Ag Kühlvorrichtung zum Temperieren unterschiedlicher Komponenten einer Druckmaschine oder einer Werkzeugmaschine mit einem Kältemittelkreislauf sowie korrespondierendes Verfahren
DE102015202183A1 (de) * 2015-02-06 2016-08-11 Koenig & Bauer Ag Temperieraggregat zur Temperierung von Funktionsteilen einer Druckmaschine sowie Druckanlage mit einer Druckmaschine und einem Temperieraggregat
CN105799311B (zh) * 2016-03-21 2018-04-13 安徽工程大学 一种印刷机印版温度控制装置及其温度控制方法
DE102018001132A1 (de) * 2018-02-12 2019-08-14 Harburg-Freudenberger Maschinenbau Gmbh Verfahren und Vorrichtung zur Ventilsteuerung
DE102018113959A1 (de) * 2018-06-12 2019-12-12 Baldwin Technology Gmbh Druckmaschinen-temperierungsvorrichtung und verfahren zum temperieren von farbwerken und von feuchtmittel einer offset-druckmaschine
CN109677103A (zh) * 2019-03-05 2019-04-26 昆山侨通印务有限公司 一种胶印机水箱水温地下降温系统
EP4013618A1 (fr) 2019-08-15 2022-06-22 Bobst Bielefeld GmbH Unité de réfrigération pour une machine d'impression et machine d'impression

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WO2009059787A3 (fr) 2009-11-12
EP2209631A2 (fr) 2010-07-28
WO2009059787A2 (fr) 2009-05-14
DE102007053080A1 (de) 2009-05-20
CN101883679B (zh) 2013-06-05
EP2527147B1 (fr) 2014-06-04
CN101883679A (zh) 2010-11-10
EP2209631B1 (fr) 2012-07-04
US20110088879A1 (en) 2011-04-21

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